Pivoting deflector water balance system for centrifugal extractor apparatus



W. K. COMPANS PIVOTING DEFLECTOR WATER BALANCE SYSTEM Jan. 28, 1964 FORCENTRIFUGAL EXTRACTOR APPARATUS 4 Sheets-Sheet 1 Filed Oct. 10, 1960 mm8 mm 3 INVENTOR- WI LFRIED KARL COMPANS t j ATTORNEYS Jan. 28, 1964 w.K. COMPANS 3,119,773

PIVOTING DEFLECTOR WATER BALANCE SYSTEM FOR CENTRIFUGAL EXTRACTORAPPARATUS Filed Oct. 10, 1960 4 Sheets-Sheet 3 X Ln ml Q LL.

INVENTOR. WILFRIED KARL COMPANS Jan. 28, 1964 w. K. COMPANS 3,119,773

FIVOTING DEFLECTOR WATER BALANCE SYSTEM FOR CENTRIFUGAL EXTRACTORAPPARATUS Filed 001;. 10, 1960 4 Sheets-Sheet 4 FIGB F169 INVENTOR.

Wl LFRIED KARL COMPANS ATTORNEYS United States Patent 3 119 773 PIVOTINGDEFLETGlZ WATER BALANCE SYSTEM FOR CENTRIFUGAL EXTRACTOR APPARATUSWllfried K. Compans, St. Joseph, Mich., assignor to WhirlpoolCorporation, St. Joseph, Mich, a corporation of Delaware Filed Oct. 10,1960, Ser. No. 61,623 4 Claims. (Cl. 210144) The present inventionrelates broadly to apparatus for counterbalancing unsymmetricallydistributed centrifugal forces in a rotating body, and is moreparticularly concerned with a laundry apparatus wherein a horizontal orsubstantially horizontal axis type drum containing a batch of materialsto be laundered my be rotated at high speeds for optimum waterextraction, without the detrimental effects caused by excessiveuncontrolled vibrations.

The principles of the present invention are generally applicable to anybalancing system and method wherein it is desired to counterbalanceunsymmetrically dis osed centrifugal forces generated because ofunbalance in a rotating body, however, because the principles of thepres ent invention find a particularly useful application to a laundrymachine and method, the invention is described and illustrated inconnection with a specific laundry machine and method associated withdomestic utilization such as a typical home laundry appliance.

From the point of view of a housewife laundry machine operator, it ishighly desirable that a laundry load be completely washed and dried inas short a time as possible. Such criterion is applicable whether theload of clothes to be laundered is to be line-dried or machine-dried. Ineither case, the length of time required to dry a particular load willbe substantially directly proportional to the quantum of liquid retainedin the material at the end of a washing cycle.

In contemporary domestic laundry appliances, including automatic washingmachines wherein clothes are washed and centrifuged, or in so-calledcombination washer-dryers wherein clothes are washed, rinsed, spun dryand tumbled dry with the application of heat energy, that part of thetotal washing and drying time preceding the tumble dry or line dryportion of the total laundering cycle time is designated as the washportion of the total cycle and consumes substantially the same amount ofactual time for all available machines. Thus, to decrease the overallwash and dry time of a particular load, the most practical substantialtime savings can be made by shortening the dry portion of the totalcycle.

The usual approach to an attempted improvement of machine dryinginvolves the consideration of increasing the drying heat input to thedryer which is somewhat undesirable from a standpoint of powerconsumption and the somewhat increased cost of operation thus incurred,but it is most undesirable from a standpoint of engineering designconsiderations which are required because of the increased power inputto the drying means.

In accordance with the principles of the present invention, a secondapproach is made which is desirable not only from a standpoint ofmachine drying, but also from a standpoint of line drying and that is toincrease the rotative cylinder speed used during the extraction part ofthe wash cycle to remove larger amounts of water from the load prior tothe beginning of the tumble or line drying of the load. By increasingthe spin speed utilized to remove additional water from the load, apower consumption rate savings of approximately 8 to 15 times may beaccomplished over the removal of this additional water by the high powerinput drying process.

With properly designed bearing and transmission systems power input isthe primary consideration that has to be made with respect to the limitof spin speed attained in driving a mass about its exact center of mass.An empty laundry receiving cylinder or drum rotated about its bearaxisparallels an optimum operating condition, but when a load is introducedinto the cylinder, the load is likely to be distributed in such a mannerthat the center of mass of the loaded cylinder will not coincide withthe cylinder bearing axis, thereby producing an unbalanced centrifugalforce which is directly proportional to the mass of the unbalancedportion of the total rotating mass, the square of the angular velocityof such unbalanced mass and the radius of the unbalanced weight from theaxis of rotation of the cylinder.

In addition to affecting the power input necessary to rotate thecylinder or drum, an unbalanced condition causes serious vibrationconditions which are even more pronounced in horizontal machines than invertical axis machines since the unbalanced force directed substantiallyopposite the gravitational forces acting on the machine may besulficiently great to actually lift the machine from its supportingsurface and produce a violent movement colloquially referred to aswalking.

Because of these problems, some contemporary laundry machines of thehorizontal axis type operate at a sufli ciently limited spin speed sothat the unbalanced loads encountered during normal operation will notproduce a sufficient amount of centrifugal force to bodily lift themachine from its support. It has also been contemplated in prior artmachines to provide control means whereby a spin mechanism will beinactivated in response to excessive motion in the apparatus, whereuponthe drum or cylinder will decelerate to a tumbling speed forredistribution of the contents thereof. In such prior art machines, thefinal spin speed is limited to a value such that the total amount ofliquid centrifugally extracted from the contents of the drum or cylinderis much less than desired. It will be readily appreciated that all suchextra retained liquid is required to be evaporated either by a longerperiod of evaporation if the goods are line dried or by consumption ofan additional supply of heat energy due to a longer drying period, ifthe goods are machine-dried.

Other forms of balancing mechanisms employed in laundry apparatuscontemplate suspension of the entire laundry machine along with anadditional mass producing dead weight within the enclosing cabinet on acomplex spring system. Such arrangements depend upon isolation of thesource of vibration, whereupon the suspended sys tem is allowed toviolently vibrate within the enclosing cabinet, with the dead weighttending to minimize the effects of the unbalanced centrifugal forces.With such prior art arrangements, it is inevitably necessary that thesize of the enclosing cabinet must be greatly increased to allow for theviolent gyratory motions of such system during operation of the machine,or the diameter of the clothes cylinder must be reduced, Where cabinetsize is a factor, to the point where the capacity of the cylinderbecomes impractical if wrinkle free drying is to be maintained.

In other forms of prior art machines, eccentric motions of the rotatingbody are sensed and located by relatively complex mechanisms whichcontrol the addition or subtraction of weights from. the rotatingcomponents of the machine, thereby to counteract the unsymmetricallydisposed centrifugal forces generated by the unbalanced conditionswithin the cylinder or drum.

In accordance with the principles of the present invention, a casing isrigidly supported by a base frame and within the casing a drum ismounted for rotation and for vibratory movement relative to the baseframe. A flow regulator or deflector is mechanically connected to themeans which mounts the dnnn for rotation within the casing, and thedeflector moves in phase with a deflection produced by an off-balanceload being rotated, and desirably the deflector or flow regulator pivotsto either interrupt or allow a flow of balancing liquid from a nozzle tobe introduced into certain of a plurality of liquid balance pocketsdisposed on the periphery of the drum, thereby effectivelycoun-terbalancing the off-balance load.

By virtue of this novel arrangement of parts, the situs of the unbalanceis automatically determined and only as much counterbalancing liquid asis required is added to the rotatingsystem of the machine.

It is accordingly an important aim of the present invention to provideimproved counterbalance control means for a rotating receptacle.

Another object of this invention lies in the provision of a balancingsystem for a rotating receptacle which adds to the rotating system onlyso much balancing liquid as is required to place the system inoperational equilibrium.

Another object of the instant invention is to provide a balancing systemfor a laundry apparatus wherein the laundry liquid may be effectivelyutilized as a balancing fluid.

. A further object of this invention lies in the provision of acounterbalancing system wherein a deflector member is mounted forpivotal movement by mounting structure which vibrates relative to casingsupporting means, the deflector being interposed in a path of fluid flowfrom a stationary nozzle member and moving in phase with a deflectionproduced by an off-balance load being rotated in an extractor drum suchthat the pivoting deflector either interrupts or allows a flow ofbalancing liquid from the nozzle to be discharged into the drum tocounterbalance unsymmetrically distributed centrifugal forces therein.

Other objects and advantages of the invention will become more apparentduring the course of the following description, particularly when takenin connection with the accompanying drawings.

In the drawings, wherein like numerals designate like parts throughoutthe same:

FIGURE 1 is a side elevational view, with parts removed and with partstaken in section, to more clearly illustrate the counterbalancing systemof this invention;

FIGURE 2 is an end elevational view, with parts removed and with partstaken in section, showing in further detail a laundry machine embodyingthe balancing system of the present invention;

FIGURE 3 is a fragmentary sectional view of the deflector mounting meansand injection intake segment which connects with a liquid balance pocketto receive balancing liquid from the illustrated nozzle when anoff-balance condition is present;

FIGURE 4 is a vertical sectional view taken substantially along the line44 of FIGURE 3, and showing certain details of the pivotal mounting forthe deflector;

FIGURE 5 is a fragmentary end elevational view of the pivoting deflectorand mounting means therefor which internupts or permits liquid flow fromthe illustrated nozzle into certain of a plurality of the liquid balancepockets; and

'FIGURES 6 to 9 are more or less diagrammatic illustrations showing inpart a preferred nozzle position and relationship between an off-balanceload and the angle between said load and the deflection produced therebyduring a complete revolution of the extractor drum.

Referring now first to FIGURES 1 and 2, there is shown and designatedgenerally by the numeral 10 a domestic laundry appliance which may takethe form of a so-called combination washer-dryer. Certain structuralportions of the laundry appliance have been omitted in the interest ofclarity of illustration and since such portions are not essential to thepresent invention.

In the exemplary structural organization shown, the machine 10 isprovided with a base plate or support structure indicated at 11. Anenclosing cabinet (not shown) having side, front, and back walls plus atop wall is attached to the upright sides of the base plate 11. Thefront wall provides access at 12 by means of which a batch of materialsto be laundered may be placed in or withdrawn from a treatment zoneformed Within the machine 10.

The cabinet is supported upon front and rear legs 13 and 14 which aremounted on the base plate or support structure 11, and upon the baseplate 11 there is fixedly mounted a drum mounting structure designatedat 15, and which may take the form of a pair of spaced uprights 15a and15b. The base portion of the cabinet 11 further fixedly supports, asshown in FIGURE 1, a casing 16 spaced within the cabinet and shapedalong its lower portion as indicated in FIGURE 2 by the numeral 16a toprovide a sump.

Mounted for rotation within the casing 16 and for vibratory movementrelative to the casing 16 and base plate 11 is a perforated drum orcylinder 17 having a passaged front wall 17a and closed rear wall 17bconnecting generally centrally thereof with shaft means 18 received atits opposite end in relatively fixed bearing means 19. The bearing means19 is attached in any suitable manner to a generally horizontal supportor pylon member 21 connected at its opposite ends to the upright members15a and 15b, and constituting the herein provided means for mounting thedrum 17 for rotation within the casing 16 and for vibratory movementrelative to the casing 16 and base plate 11. As will be later describedin further detail, rotation of the drum 17 with an unbalanced loadtherein causes the pylon member 21 to vibrate in opposed horizontaldirections as indicated by the arrows 22, and in the absence of theapplication of counterbalancing forces, such vibration may be suflicientto cause the machine 10 to actually walk upon the floor. This situationcan exist whether or not a supporting structure of the characterindicated at 15 is employed, and it can accordingly be appreciated thatthe supporting means 15 can take the form of an A frame or any otherbasket or drum mounting arrangements.

The drum or basket 17 is provided with recess means at a plurality ofcircumferentially spaced points on its periphery to accommodate mountingin such recesses a liquid balancing. receptacle, of which three areprovided in the illustrative embodiment shown and designated therein bythe numerals 23a-c. Each balancing receptacle is of essentiallyidentical construction and comprises a generally trough-shaped traymember having a wall 24 spaced radially outwardly of an imperforate wallportion 25 formed on the drum 17 at the recessed area. Each receptacle23a-c further includes side walls 26, and in the generally diagrammaticshowing of FIGURE 1, front and rear walls 27 and 28. The front walls 27desirably have drain openings of minimal dimension adjacent theperforate wall portion 25 (not shown) to afford draining after thedrying cycle.

Illustratively, the receptacles 23a-c and injection intake structuretherefor may take the form shown in FIGURE 3, to which reference is nowmade. The rear wall 28 of each receptacle 23 and rear wall 17b of thedrum 17 may be passaged to receive a connector member 29 communicatingwith an annular fluid guide member 30 secured as at 31 to the drum rearwall 17b. The trough-like guide ring 30 is mounted to be in fluidreceiving communication with an inlet assembly generally designated bythe numeral 32, and desirably provided by a generally U-shaped ringmember divided at 33 (FIGURE 2) to provide three inlet segments 32a-cextending through of arc on the rear wall 17b of the drum 17. Three 120segments have been found advantageous in practice, and the specificreasons therefor will be discussed hereinafter.

As appears in FIGURE 3, the injection intake ring 32 has a pair ofspaced wall portions 34 and 35 connected by a radial wall 36 aperturedat 37 at circumferentially spaced locations to communicate the inletsegments 32ac with a particular balance receptacle 23a-c during thecounter-balancing action. As also appears in FIGURE 3, the injectionintake member 32 is welded or otherwise secured along its Wall portion34 to a plate portion 38 connected to the drum rear wall 17b.

The drum 17 is rotatively driven within the casing 16 in any desiredmanner, and illustratively there may be provided motor means 39 providedwith a shaft 44) mounting pulley means 41 about which is trained a belt42 also wrapping a pulley 43 on the drum drive shaft 18. Desirably, themotor means 39 connects with transmission means having low and highspeed capabilities, and shifting or clutching means preferably form apart of the transmission means in order that continued acceleration ofthe basket or drum 17 can be terminated during counterbalancing. This,however, forms no part of the instant invention and the details thereofare accordingly not illustrated.

It has been earlier noted that in the balancing systems of the prior artit has been proposed to inactivate the spin mechanism in response toexcessive motion in the laundry apparatus, to suspend the entire laundrymachine along with an additional mass producing dead weight within theenclosing cabinet on a complex spring system, or to sense and locatedeccentric motions of the rotating body by relatively complex mechanismswhich control the addition or subtraction of weights from the rotatingcomponents of the machine. Some of the numerous disadvantages of thesesystems have been referred to hereinabove.

The mechanism provided in accordance with the principles of thisinvention and which eliminates the noted deficiencies of the prior artcomprises first a nozzle assembly generally designated by the numeral 45and deflector means or flow regulator means designated in its entiretyby the numeral 46. The nozzle assembly 45 in: cludes a conduit portion47, as shown in FIGURE 1, communicating with a liquid source, whichdesirably is the laundry liquid in the sump 16a in order that liquid orwater be supplied to the nozzle assembly at uniform pressures. Liquidflow from the sump 16a is of course under control of pump means (notshown) in the man.- ner known to the art.

The nozzle assembly 45 further includes a nozzle 43 connected to theconduit or hose portion 47 by a clamp? ing member 4-9. As appears inFIGURE 5, the nozzle assembly 45 ischaracterized by a narrow elongatednozzle outlet 50 registering with a slotted opening (FIG- URE 3) in rearwall 16b of the casing 16. The nozzle assembly 45, and; particularly thenozzle 48, as shown in FIGURE 1, thereof, is stationarily mounted tocasing structure and this can be accomplished in any desired 11 .1 .6

The deflector or interruptor member 46 is generally flat and more orless paddle-shaped, and is formed tc provide a main body portion 51 andend portion 52 which is provided with a relatively narrow elongated slot55 to register with the opening 59 in the nozzle 48 during thecounterbalancing action. Of course, the deflector member 46 need notbeslotted, and instead the end portion 52 thereof .could be of reducedwidth to permit liq uid discharge on the proper side of the end portionduring ,counterbalancing.

The pivotal mounting for the deflector of interruptor member 46' isillustrated in FIGURES 3, 4 and 5, and as appears therein bracket means55 is bolted; or otherwise secured at 56 to lower wall portion 21a ofthe pylon member 21. The bracket means 55 is formed with a dependentapertured tongue portion 55a (FIGURE 5 and press fit or otherwisetightly carried in the aperture in the tongue portion 55a is pin means57. The pin means or pivot shaft 57 receives thereon an aperturedbearing member 58, which as appears in FIGURE 4, is grooved at itsopposite ends to provide spaced track portions 58a engageable with anupstanding generally U-shaped portion 59a on bracket means 59. In thismanner, during assembly the bearing member 58 is slid into engagementwith the U-shaped portion 59a on the bracket member 59.

The bracket means or bottom adjustment bracket 59 is provided with a hubportion 5% (FIGURE 3) which is freely rotatable upon shaft means 60which in turnis freely received in sleeve means 61 having bearing meansall of which are rigidly supported by a plate member 62 provided withstrengthening ribs 62a and attached at 6 to the casing rear wall 161;,

The shaft means 60 co-rotatably mounts a hub member 64 to which by screwmeans or the like 65 the leg portion 51 of the deflector member 46 isconnected at one end. If desired, the hub portion 64 and end portion ofthe deflector leg 51 may be provided with mating screw receivingopenings, and the means for attachment of the hub member to the shaft 60may be pin means as indicated at -66.

The pivotal mounting arrangement for the deflector member 46 furtherincludes bracket means 67 (FIGURE 5) shaped to provide a hub or shaftreceiving portion 67a. and an outwardly extending arm portion 67b. Thebracket hub portion 67a is rigidly connected to the shaft means 60, asindicated in FIGURE 4 at 68, and the bracket arm portion 67b is slottedas at 69 in the same view to receive adjustment bolt means 70. The boltmeans 7t} is rigidly connected to leg portion 59c of the bracket member59, as at 71 and the bolt registers with a slot portion 72 of legportions 590 as shown in FIG: URE 4. The leg portion 590 of the bracketmember 59 is integral with the bracket 59 and the hub portion 5%thereof. Threadably received upon the bolt means '70 and bearing againstopposite faces of thearm portion 6% of the bracket means 67 is a pair ofnut means 73a and 73b, which function in a manner to be described indetail hereinafter to adjust the position of the deflector member 46 sothat the nozzle opening 54} injects liquid through the deflector slot 53at the proper times.

It may now be seen that by the pivotal mounting arrangement describedthat when the pylon member 21 vibrates in either of the directionsindicated by the arrows 22 thereon in FIGURE 2, caused by the presenceof an unbalanced load in the rotatable drum 17, the bracket member 59pivots or swings to cause corresponding movements of the bracket member67, which by its rigid connection to the shaft means 60, rotates theshaft and pivots or swings the connecting deflector member 46.

Thus, the pivoting deflector means for controlling the flow of liquidbetween the nozzle 48 and the pockets 23a-c have, in effect, a linkageprovided by the bracket members 59, 55 and 67 so that such bracketmembers may be referred to herein as first, second and third linkagemeans, respectively.

Prior to describing the manner of coordinating the deflector positionwith a particular balance receptacle 2;} during rotation of anunbalanced load in the drum or cy-linder 1.7, it is desired to note thatin FIGURE 2 there is shown safety means to arrest the acceleration ofthe cylinder when severe unbalanced loads are encountered. Such meansmay comprise a leg member 75 connected to and depending from the pylonmember 21 to move therewith and correspondingly vibrate. The leg member75 may mount at its lower end pin means 76- for engagement with pinmeans 77 of switch means 78 mounted on the base plate '11. The switch'73 desirably is of the time delay type, and through suitable electricalcircuitry connects with the motor means 39 to stop the acceleration ofthe cylinder when switch 73 is opened due to the presence of a severeunbalanced load. The time delay allows the cylinder to return to tumblespeed so the load will be redistributed. After the time delay period,switch 78 will reclose and the cylinder will again accelerate.

As was stated, motion of the interrupter or deflector member 46 must betimed in a manner to permit the flow of balancing liquid into thesegment or segments 32 which supply the balancing compartment orcompartments 2;?

located diametrally opposite the off-balance load, designated in FIGURE2 as L. Applied to this same view is the designation BB identifying thehorizontal centerline of the machine or the line of structure motion,and in investigations which have been conducted it has been found thatas the elf-balance load L passes the line BB on one side of the machine,the deflection of the pylon member 21 on this same side of the machineis not at its maximum value. This diflerence is referred to herein asthe lag angle between the off-balance load and the deflection producedthereby. The lag angle is partly determinative of the angularrelationship between a balance compartment and its corresponding inletsegment.

By measurement under test conditions, there can be de termined the meantotal angle of lag over the balancing speed range, or otherwise stated,the average value of the lag angle from the speed at which thecentrifugal force of the load in the drum or cylinder overcomes gravityto the maximum cylinder speed. This value when there is then addedthereto the angle of advance of the center of a particular segment 32 inrelation to the center of its respective compartment 23 must equal anangle, identified in FIGURE 2 as alpha and which lies between thehorizontal centerline B--B and the indicated radial line CC extendingfrom the center of the drum 17 and passing through the center of thenozzle opening 50. This is more thoroughly explained in conjunction withthe explanation of FIGURES 6-9.

It may be observed from FIGURE 2, and as was earlier described, threeinlet segments 32a-c and a corresponding number of balancingcompartments 23a-c are employed. Such an arrangement has been foundadvantageous in order to initiate the counterbalancing action in theearly phases of pylon deflection, while still not providing large inletsegments. To explain, it is of course desirable to use as small a volumeof liquid for balancing purposes as is possible, and to direct thisrelatively small volume of liquid into the correct balancingcompartments as rapidly as possible. As well, as the volume of thebalance compartments increases, there is then less volume within thecylinder '17 for the load.

Since the direction of cylinder rotation in FIGURE 2 is clockwise, andsince obviously because of gravity conditions the balancing liquidshould be delivered to the cylinder 17 beneath the horizontal centerlineBB, the nozzle 48 is positioned in the lower righthand corner of thecylinder circumference, as shown, or generally between 21 three oclockand six oclock position. Accordingly, balancing will take place onlywhen the pylon member .21 deflects to the left of the verticalcenterline. If a zero lag angle is assumed, it can be seen that when theoff-balance load L in clockwise rotation passes the vertical centerlinebeneath the horizontal centerline BB, deflection of the pylon member tothe left begins. Now, if inlet segments 90 in arcuate length wereemployed, the injection of liquid into the inlet segments would notbegin until the off-balance load had rotated 45. According to the lawsof simple harmonic motion, a 45 rotation of the off-balance load fromthe vertical centerline corresponds to a pylon deflection of about 67%of the maximum value achievable with an otf-balance load. It is thusapparent that with four 90 inlet segments and a corresponding number ofbalancing compartments, balancing could not begin until 67% of maximumpylon deflection had been achieved, and such a relatively highpercentage of maximum deflection would obviously be undesirable.

However, when three balance compartments 23ac are employed, balancingbegins after the off-balance load L has traveled only 30 from thevertical centerline, again assuming a zero lag angle. A 30 travel of theoffbalance load corresponds to only 50% of the maximum deflection of thepylon member 21 due to that off-balance load. Accordingly, three balancetanks ZCia-c provide an optimum compromise between pylon pre-travelbefore balancing begins and the required balance tank liquid capacity.

An important angular relationship exists between each balance tank andits respective inlet segment. This can probably be best understood byreference to FIGURES 6 to 9, in each of which the legend alphadesignates the location of the nozzle 43 beneath the horizontalcenterline and the radial line from the center of the cylinder passingthrough the center of the nozzle. In FIGURES 6 and 8 there is as wellidentified by the legend A the average lag angle by which, for thisexample, the unbalanced load leads the deflection it produces. Inaddition, it may be observed that like numerals from the preceding viewshave been employed to designate the drum or cylinder 1'7, balancecompartments 23a-c, inlet segments 32zz-c, nozzle opening 50 andunbalanced load L.

In the discussion now to 'follow, the exemplary conditions employedinclude injection of liquid from the nozzle opening 50 on pylon motionto the left only, a nozzle location at the angle alpha of 60 from thehorizontal centerline B--B, an arc of injection of and an angle A of 30by which the off-balance load L leads the deflection caused thereby. Aswell, for purposes of illustration, the off-balance load is shown aslocated between the balance compartments 23a and 23b, although of courseeflective counterbalancing is provided regardless of the load position.Since the balance compartment 230 is diametrally opposite theoff-balance load L, the objective achieved by this invention is todirect the smallest volume of water in the shortest period of time tothe balance tank 23c.

In FIGURE 6 the conditions existing are zero pylon motion, and with thestated lag conditions, the off-balance load L is at an angle A of 30from the vertical centerline. In this position the deflector orinterrupter member 46 is disposed in fluid blocking relation to thenozzle opening 50, essentially as shown in FIGURES 2 and 3.

In FIGURE 7 it may be seen that the off-balance load L has rotated 30from the position of FIGURE 6, and in order to limit the injection tothe desired 120 arc, injection is now initiated. Since it is alsodesirable that all of the balancing fluid be directed to balancingcompartment 230, the divider 33 between the inlet segments 32a and 320must be directly beneath the nozzle opening 50. This is shown in FIGURE7, and at this point in the counterbalancing cycle the deflection of thepylon member 21 is at 50% of its maximum value. Injection begins intoinlet segment 32c.

Maximum pylon deflection to the left is present in the illustrativepresentation of FIGURE 8, and this occurs when the ofi-balance load L isapproximately 30 above the horizontal centerline BB. At this point thedeflector slot 53 is precisely aligned with the nozzle opening 50 formaximum injection, and the inlet segment 320 has been receivingcounterbalancing fluid for 60 of drum rotation, as indicated in FIGURE 8by the legend F. The centerline of inlet segment 320 is on line with thenozzle opening.

During the next 60 of cylinder rotation essentially the same actiontakes place as described, with the exception that the motion of thepylon member 21 is to the right in FIGURE 2. FIGURE 9 is illustrative ofthe conditions when approximately of cylinder rotation has occurred, or120 of injection. The baflie or divider 33 separating the inlet segments32c and 32b is of course at this time directly beneath the injectornozzle 50. Injection of counterbalancing fluid then terminates as thepylon member 21 continues movement to the right, to place the deflectorend portion 52 in fluid blocking relation with the nozzle opening 50.

It is to be observed from an examination of FIGURES 6 to 9 that all ofthe liquid injected during the 120 arc of rotation is confined to theinlet segment 32c, so that all balancing fluid is introduced into thebalancing compartment 230, which as earlier stated, is the correctcompartment for eifective counterblanacing of an oilbalance load whenlocated as originally assumed in connection with FIGURE 6. This showsthat for this example, counterbalancing has been achieved in anefficient manner by using a minimum of counterbalancing fluid.

It is apparent from FIGURE 8' that to accomplish the most efficientcounterbalancing under the illustrative conditions indicated, thecenterline of the inlet segment must be located at an ange of alpha-Aahead of or leading the centerline of the corresponding compartment intowhich counterbalancing fluid is to be introduced. This is the caseregardless of the values of the true angles. If there was no lag anglein the system, the centerline of the balance tank or compartment 23c andthe trailing edge of the corresponding inlet segment would coincide. Ofcourse, if the nozzle opening was targeted in a direction other thandirectly downwardly, as is indicated in FIGURES 6 to 9, compensationwould be necessary for the different target angle.

The adjustment means 70 is provided so that the deflector '46 can beadjusted so that slot 53 indexes in front of nozzle 50 at the preciseinstance as indicated in the explanation of FIGURES 69.

For purposes of simplicity in FlGURES 6-9 the unbalanced load L waspositioned so that with a 120 arc of injection all of thecounterbalancing fluid would go into compartment 23c. If it is desiredfor illustrative purposes, to place the unbalanced load L in a differentlocation, it will be found that the same inlet segmentcompartmentrelationship will allow the newly positioned unbalanced load to bebalanced using a minimum of counterbalancing fluid. Of course, for anyposition of the unbalanced load other than midway between two balancingcompartments the same set up would assure the proper proportioning ofcounterbalancing fluid to the two compartments necessary for properbalancing.

It is believed now apparent from the preceding discussion that there isherein provided a counterbalancing system of rapid and accurate responsewhich is reliably phased by means of relatively simple adjustments inthe pivotal mounting for the deflector structure. It was noted that thedeflector need not be slotted, and of course, other modifications andvariations can be effected without departing from the novel concepts ofthis invention.

The embodiments of the invention in which an exclusive property orprivilege is claimed are defined as follows:

l. Centrifugal extractor apparatus comprising,

supporting means,

a receptacle,

means mounting said receptacle for rotation in said supporting means ona substantially horizontal axis, drive means for rotatably driving thereceptacle, a plurality of balancing pockets on said receptacle, meansincluding a nozzle for directing balancing liquid into the pockets,

said supporting means including a horizontal member capable ofhorizontal vibrational movement, and means for controlling the flow ofliquid between said nozzle and said pockets comprising,

a shaft journaled on said supporting means, a deflector for interruptingthe flow of liquid from the nozzle and connected to said shaft, a firstlinkage means freely rotatable on said shaft, a second linkage meansrigidly connected to said horizontal member, means including a bearinginterconnecting said first and second linkage means, a third linkagemeans corotatably connected to said shaft, and adjustable connectionmeans between said first and third linkage means, whereby said thirdlinkage means swings with said first linkage means upon vibrationalmovement of the horizontal member to rotate the shaft and swing saiddeflector relative to said nozzle.

2. Centrifugal extractor apparatus as defined in claim 1, said deflectorcomprising a generally flat main body portion connected to said shaftand having an end portion extending from said body portion to registerwith said nozzle. 3. Centrifugal extractor apparatus as defined in claim2, said deflector end portion having a narrow elongated slot formedtherein through which balancing liquid is directed when in register withsaid nozzle. 4. Centrifugal extractor apparatus as defined in claim 1,said adjustable connection means comprising arm portions on said firstand third linkage means, bolt means operatively connecting said armportions, and nut means to lock said arm portions at selected positionsof adjustment, thereby to index the deflector relative to said nozzle.

References Cited in the file of this patent UNITED STATES PATENTS Re.24,140 Kahn Apr. 10, 1956 2,584,942 Thearle Feb. 5, 1952 2,603,982 Daviset al. July 22, 1952 2,760,383 De Moss Aug. 28, 1956 3,080,059 Scott etal. Mar. 5, 1963

1. CENTRIFUGAL EXTRACTOR APPARATUS COMPRISING, SUPPORTING MEANS, ARECEPTACLE, MEANS MOUNTING SAID RECEPTACLE FOR ROTATION IN SAIDSUPPORTING MEANS ON A SUBSTANTIALLY HORIZONTAL AXIS, DRIVE MEANS FORROTATABLY DRIVING THE RECEPTACLE, A PLURALITY OF BALANCING POCKETS ONSAID RECEPTACLE, MEANS INCLUDING A NOZZLE FOR DIRECTING BALANCING LIQUIDINTO THE POCIKETS, SAID SUPPORTING MEANS INCLUDING A HORIZONTAL MEMBERCAPABLE OF HORIZONTAL VIBRATIONAL MOVEMENT, AND MEANS FOR CONTROLLINGTHE FLOW OF LIQUID BETWEEN SAID NOZZLE AND SAID POCKETS COMPRISING, ASHAFT JOURNALED ON SAID SUPPORTING MEANS, A DEFLECTOR FOR INTERRUPTINGTHE FLOW OF LIQUID FROM THE NOZZLE AND CONNECTED TO SAID SHAFT, A FIRSTLINKAGE MEANS FREELY ROTATABLE ON SAID SHAFT, A SECOND LINKAGE MEANSRIGIDLY CONNECTED TO SAID HORIZONTAL MEMBER,